Classifications

• • B—PERFORMING OPERATIONS; TRANSPORTING
  • B60—VEHICLES IN GENERAL
  • B60G—VEHICLE SUSPENSION ARRANGEMENTS
  • B60G15/00—Resilient suspensions characterised by arrangement, location or type of combined spring and vibration damper, e.g. telescopic type
  • B60G15/02—Resilient suspensions characterised by arrangement, location or type of combined spring and vibration damper, e.g. telescopic type having mechanical spring
  • B60G15/06—Resilient suspensions characterised by arrangement, location or type of combined spring and vibration damper, e.g. telescopic type having mechanical spring and fluid damper
• • B—PERFORMING OPERATIONS; TRANSPORTING
  • B60—VEHICLES IN GENERAL
  • B60G—VEHICLE SUSPENSION ARRANGEMENTS
  • B60G15/00—Resilient suspensions characterised by arrangement, location or type of combined spring and vibration damper, e.g. telescopic type
  • B60G15/02—Resilient suspensions characterised by arrangement, location or type of combined spring and vibration damper, e.g. telescopic type having mechanical spring
  • B60G15/06—Resilient suspensions characterised by arrangement, location or type of combined spring and vibration damper, e.g. telescopic type having mechanical spring and fluid damper
  • B60G15/067—Resilient suspensions characterised by arrangement, location or type of combined spring and vibration damper, e.g. telescopic type having mechanical spring and fluid damper characterised by the mounting on the vehicle body or chassis of the spring and damper unit
  • B60G15/068—Resilient suspensions characterised by arrangement, location or type of combined spring and vibration damper, e.g. telescopic type having mechanical spring and fluid damper characterised by the mounting on the vehicle body or chassis of the spring and damper unit specially adapted for MacPherson strut-type suspension
• • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
  • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
  • F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
  • F16C19/00—Bearings with rolling contact, for exclusively rotary movement
  • F16C19/02—Bearings with rolling contact, for exclusively rotary movement with bearing balls essentially of the same size in one or more circular rows
  • F16C19/10—Bearings with rolling contact, for exclusively rotary movement with bearing balls essentially of the same size in one or more circular rows for axial load mainly
• • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
  • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
  • F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
  • F16C33/00—Parts of bearings; Special methods for making bearings or parts thereof
  • F16C33/30—Parts of ball or roller bearings
  • F16C33/58—Raceways; Race rings
• • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
  • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
  • F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
  • F16C33/00—Parts of bearings; Special methods for making bearings or parts thereof
  • F16C33/30—Parts of ball or roller bearings
  • F16C33/58—Raceways; Race rings
  • F16C33/588—Races of sheet metal
• • B—PERFORMING OPERATIONS; TRANSPORTING
  • B60—VEHICLES IN GENERAL
  • B60G—VEHICLE SUSPENSION ARRANGEMENTS
  • B60G2204/00—Indexing codes related to suspensions per se or to auxiliary parts
  • B60G2204/10—Mounting of suspension elements
  • B60G2204/12—Mounting of springs or dampers
  • B60G2204/128—Damper mount on vehicle body or chassis
• • B—PERFORMING OPERATIONS; TRANSPORTING
  • B60—VEHICLES IN GENERAL
  • B60G—VEHICLE SUSPENSION ARRANGEMENTS
  • B60G2204/00—Indexing codes related to suspensions per se or to auxiliary parts
  • B60G2204/40—Auxiliary suspension parts; Adjustment of suspensions
  • B60G2204/418—Bearings, e.g. ball or roller bearings
• • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
  • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
  • F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
  • F16C2326/00—Articles relating to transporting
  • F16C2326/01—Parts of vehicles in general
  • F16C2326/05—Vehicle suspensions, e.g. bearings, pivots or connecting rods used therein

Definitions

• the invention relates to a vehicle suspension stop, provided with a ball bearing.
• the use of plate washer bearings stamped in suspension stops is illustrated for example by the document FR2918138.
• one of the washers materializing the raceways called the lower washer, bears on a plastic support constituting an interface with a suspension coil spring of the wheel, the other washer, said upper, being supported under a cover attached to the vehicle body.
• the raceways have in section an arcuate profile whose opening angle is 60 °.
• the raceway of the lower washer is open radially inward and has no rim that can limit radially inward movement of the balls. This is reflected by the fact that the arc of the raceway circle of the lower washer is in no point tangent to a plane perpendicular to the axis of symmetry of revolution of the raceway.
• the raceway of the upper washer is open radially outwardly and has no rim which can limit the movement of the balls radially outwards, which geometrically results in the fact that the arc the circle of the raceway of the upper washer is not at any point tangent to a plane perpendicular to the axis of symmetry of revolution of the upper raceway.
• the stresses of such a stop are multidirectional and asymmetrical, which results in very unequally distributed constraints between the balls. If the abutment is undersized with respect to these stresses, one can then note an opening of the bearing and radial movements of the balls which can ultimately result in an expulsion of a ball.
• the potential malfunction of the bearing may also be manifested by chattering of the balls with sudden loss of adhesion interrupting the bearing. rolling of some of the balls on the raceways and causing sliding causing rapid wear.
• the plastic parts constituting the spring support and the cover if they are undersized, can also undergo deformations and come into contact with one another, which accentuates the dysfunction of the stop.
• the invention aims to overcome the disadvantages of the state of the art and in particular to provide a bearing having increased rigidity and a better resistance to radial forces.
• a bearing according to the invention of the general type comprising: a lower washer forming a lower raceway, an upper washer having an upper raceway, and balls rolling on the lower and upper races to ensure the relative rotation of the upper and lower washers about a geometric axis of rotation of the bearing.
• the terms “lower washer” and “upper washer” are used with reference to a preferred use of the bearing according to the invention, namely within a stop of vehicle suspension, in which the axis of rotation of the bearing is close to the vertical and the upper washer is disposed axially above the lower washer.
• the terms “superior” and “inferior” are to be understood as an arbitrary designation of pucks.
• the bearing according to the invention is more specifically of the angular contact type, which, in the context of the present application, means that the geometry of the bearing is such that in any cutting plane containing the geometric axis of rotation of the bearing, the lower raceway forms a lower arc that defines a center of lower axial curvature, the upper raceway forms an upper arc that defines a center of higher axial curvature, the centers of lower and upper curvature being located on an oblique geometric axis forming with the geometrical axis of rotation an oblique angle of value between 5 ° and 65 °, and preferably between 20 ° and 50 °.
• the angle of obliqueness is of the order of 35 °.
• the geometry of the lower raceway is characterized in that in any cutting plane containing the geometric axis of rotation of the bearing, the lower arc has two ends defining an opening angle. of a value greater than or equal to 80 ° and a tangent situated in a lower plane perpendicular to the axis of rotation at a lower tangent point defining with the end of the nearest lower circular arc a portion of the arc of lower circle with an opening angle greater than or equal to 10 °.
• the lower raceway is particularly enveloping, which allows to confine the balls radially.
• the lower arc extending on either side of the lower tangent point, the path can take centrifugal and centripetal radial forces.
• the bearing is considered off load, the axis of rotation of the bearing being coincident with the axis of symmetry of revolution of the lower raceway and with the axis of symmetry of revolution of the raceway. superior.
• the raceways are the surfaces of the upper and lower washers intended to be in contact with the balls, and may optionally be subject to a treatment intended to increase their hardness, for example a heat treatment. In a known manner, they are also preferably subjected to a surface protection treatment against corrosion and rectification or superfinishing to reduce their roughness.
• the geometry of the upper race is characterized in that in any section plane containing the geometric axis of rotation of the bearing, the upper arc has two ends defining an opening angle of greater value.
• the upper raceway is also particularly enveloping, which allows to confine the balls radially between the two washers.
• the lower washer is made of a sheet, for example a stamped sheet.
• the lower race is a deep groove, but compatible with stamping.
• the lower washer may be provided with a cylindrical lower stiffening skirt.
• the upper washer may also consist of a sheet, for example a stamped sheet and may also be provided with a cylindrical upper stiffening skirt.
• the invention further provides a suspension stop comprising a thrust bearing as previously described, a lower bearing means for transmitting to the lower ring of the bearing forces exerted by a suspension spring and a cover for transmitting at the vehicle body the forces exerted by the spring and passing through the thrust bearing.
• the present invention by stiffening the bearing and the interface thereof with the support means, prevents the latter from moving relative to each other and / or deform; the clearances between the support means are thus controlled, particularly at the level of the baffles between the lower and upper support means, thus improving the sealing.
• the architecture of the abutment is compatible with lower and / or upper support means made of a plastic material, if necessary without a metal insert.
• the oblique angle is open towards the lower support means. This arrangement, which corresponds to the majority of vehicles, allows centering of the stop inside the lid.
• the lower washer has a cylindrical lower stiffening skirt forming a lower cylindrical bearing bearing radially against the lower bearing means.
• the lower skirt contributes to the stiffening of the washer itself and to that of the subassembly formed with the lower support means.
• the upper washer may comprise a cylindrical upper stiffening skirt forming an upper cylindrical surface bearing radially against the lid.
• the cylindrical upper skirt protrudes axially towards the lower bearing means and is preferably at least partially opposite and at a distance from the lower cylindrical skirt. The objective here is to reduce the opening between the washers, between the upper skirt and the lower washer, so as to create a pressure drop or a labyrinth opposing the entry of pollutants into the bearing.
• FIG. 1 a suspension stop according to an embodiment of the invention. invention
• FIG. 2 is a sectional view of a bearing of the abutment of FIG. 1.
• identical or similar elements are identified by identical reference signs throughout the figures.
• FIG 1 illustrates a suspension stopper 10 comprising a ball bearing 12 inserted between a cover 14 forming an interface with the vehicle body and a lower support piece 16 intended to rest, directly or with interposition of a damping elastomeric ring on the upper turn of a helical suspension spring 18.
• the cover 14 and the lower support piece 16 are made of plastic. Their shapes define an annular housing 20 for the bearing 12, which opens on the outside by a baffle 22.
• the bearing 12 consists of an upper washer 24 fixed to the lid 14, a lower washer 26 resting on the lower bearing part 16, the washers defining between them an annular volume in which are housed balls 28 retained by a cage if necessary 30.
• Each washer 24, 26 is made of a sheet, preferably formed by stamping.
• a lower race which in a known manner is a surface of revolution whose generator is, in the sectional plane of Figures 1 and 2, a circular arc C ! N f of radius greater than the radius of the balls.
• an upper raceway constituting a surface of revolution whose generator is a circular arc Cs up radius greater than the radius of the balls.
• the centers of curvature 0 Sup and Oinf of the two arcs of circles of the upper raceway and the path of lower bearing are located, in an axial sectional plane, on an axis (ZZ) oblique with respect to the axis of rotation of the bearing.
• ZZ axis
• the centers of curvatures Os up and Oi n f are also located on a cone whose generator is the preceding oblique axis, this cone also containing the centers of the balls and the pitch circle defined by the centers of the balls.
• the oblique axis makes with the axis of rotation of the bearing an angle ⁇ open downwards of 35 °, which is the half-angle of opening of the cone mentioned above.
• the arc Ci n t of the lower race has an opening angle ⁇ ⁇ important, at least 80 °. This allows a large wrapping of the balls.
• n f constitutes a nf inflection point of the profile of the inner surface of the lower washer 26.
• ⁇ ⁇ are intersecting at a point Ai n t located on the side of the plane Pi n f opposite to the arc C
• the washer 26 is extended radially downwards by a cylindrical skirt 32. As can be seen in FIG. 1, this cylindrical skirt 32 is in radial abutment against a cylindrical bearing surface 34 of the lower bearing piece 16.
• cylindrical skirt 32 increases the moment of inertia of the lower washer 26 and contributes to its stiffening, especially in the torsional deformation and flexion modes. Moreover, the cylindrical skirt 32 contributes to the stiffening of the subassembly constituted by the lower washer 26 and by the lower bearing part 16.
• the specific profile of the upper race can be described by similar geometric considerations .
• the arc of the raceway of the upper ring 24 has an opening angle cs U p important, at least 80 °. This allows a large wrapping of the balls 28.
• the outer radial end of the circular arc Cs up constitutes a point of inflection l Su p of the profile of the inner surface of the upper washer 24.
• the two tangents T SUP _E and T Supj are intersecting at a point As up located on the side of the plane Ps U p opposite to the circular arc Csup of the upper raceway.
• angles Su pj and 0SU P _E must be, in absolute value, the largest possible. In practice, it can be obtained by stamping angles verifying: e Su p j > + 60 °
• the inner radial end of the Cs up arc constitutes a point of inflection of the profile of the inner surface of the lower washer.
• the upper washer 24 is extended radially downwards by a cylindrical skirt 36. As seen in FIG. 1, this cylindrical skirt 36 is in radial abutment against a cylindrical bearing surface 38 of the lid 12.
• the cylindrical skirt 36 increases the moment inertia of the upper washer 24 and contributes to its stiffening, especially in the modes of deformation in torsion and bending. Furthermore, the cylindrical skirt 36 contributes to the stiffening of the subassembly constituted by the upper washer 26 and the cover 14. Furthermore, the two cylindrical skirts 32, 36 define a narrow annular passage constituting a pressure drop.
• each point of the lower arc Ci n f has an image on the upper arc of the circle, it is say a symmetrical point by a central symmetry whose center the center of a ball.
• this condition is realized if the straight lines T SUP _E and T

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• Engineering & Computer Science (AREA)
• General Engineering & Computer Science (AREA)
• Mechanical Engineering (AREA)
• Rolling Contact Bearings (AREA)
• Medicines That Contain Protein Lipid Enzymes And Other Medicines (AREA)
• Pharmaceuticals Containing Other Organic And Inorganic Compounds (AREA)
• Medicinal Preparation (AREA)
• Support Of The Bearing (AREA)
• Fluid-Damping Devices (AREA)

Priority Applications (6)

Applications Claiming Priority (2)

Publications (1)

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Family Applications (1)

Country Status (9)

Cited By (1)

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Citations (5)

Family Cites Families (10)

• 2009
  • 2009-10-16 FR FR0904977A patent/FR2951512A1/fr not_active Withdrawn
• 2010
  • 2010-10-14 JP JP2012533667A patent/JP2013507594A/ja active Pending
  • 2010-10-14 BR BR112012008769A patent/BR112012008769A8/pt not_active IP Right Cessation
  • 2010-10-14 US US13/501,851 patent/US20120251024A1/en not_active Abandoned
  • 2010-10-14 KR KR1020127011640A patent/KR20120112390A/ko not_active Application Discontinuation
  • 2010-10-14 WO PCT/FR2010/000685 patent/WO2011045488A1/fr active Application Filing
  • 2010-10-14 CN CN201080046679.8A patent/CN102648356B/zh active Active
  • 2010-10-14 RU RU2012119243/11A patent/RU2555372C2/ru active
  • 2010-10-14 EP EP10781936.9A patent/EP2488768B1/fr active Active

Patent Citations (6)

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